US4763473A - Arrangement for operating a diesel hydraulic drive - Google Patents

Arrangement for operating a diesel hydraulic drive Download PDF

Info

Publication number
US4763473A
US4763473A US07/035,546 US3554687A US4763473A US 4763473 A US4763473 A US 4763473A US 3554687 A US3554687 A US 3554687A US 4763473 A US4763473 A US 4763473A
Authority
US
United States
Prior art keywords
hydraulic
control
engine
microprocessor controller
output
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US07/035,546
Other languages
English (en)
Inventor
Herbert Ziplies
Heinrich Lackenberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
O&K ORENSTEIN & KOPPEL AKTIENGESELLSCHAFT A CORP OF GERMANY
CNH Industrial Baumaschinen GmbH
Original Assignee
O&K Orenstein and Koppel GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by O&K Orenstein and Koppel GmbH filed Critical O&K Orenstein and Koppel GmbH
Assigned to O&K ORENSTEIN & KOPPEL AKTIENGESELLSCHAFT, A CORP. OF GERMANY reassignment O&K ORENSTEIN & KOPPEL AKTIENGESELLSCHAFT, A CORP. OF GERMANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: LACKENBERG, HEINRICH, ZIPLIES, HERBERT
Application granted granted Critical
Publication of US4763473A publication Critical patent/US4763473A/en
Assigned to CNH BAUMASCHINEN GMBH reassignment CNH BAUMASCHINEN GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: O&K ORENSTEIN & KOPPEL
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/2025—Particular purposes of control systems not otherwise provided for
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
    • F02D29/04—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to an arrangement for operating a hydraulic drive, in general, and to an arrangement for operating a diesel-hydraulic drive on a construction machine in limit-load control with a microprocessor controller in which the installed hydraulic power is greater than the rated output of the diesel engine, in particular.
  • the hydraulic power which can be taken off is reducible; in the case of non-output loading, after a selectably predetermined time the diesel engine (1) can be switched to idling speed of rotation and hydraulic displacement pumps (2) can be operated with minimum delivery oil quantity; and the adjustable hydraulic displacement pumps (2) can be adjusted in accordance with selectably predeterminable output curves.
  • An advantage of the invention resides in the fact that the driving diesel engine of the construction machine can be operated with maximum efficiency.
  • the diesel engine (1) is coupled mechanically to a speed-of-rotation generator (9), the output voltage of which is fed as an input variable to the microprocessor controller (6).
  • the diesel engine (1) is equipped with a temperature sensor (10), the measurement values of which are fed as an input variable to the microprocessor controller.
  • control lines (16) of the pilot-control hand levers (12) are connected via change valves (13) with a pressure switch (11), the position report signal of which is fed as an input value to the microprocessor controller (6).
  • the invention provides a selector switch (15) which via the connecting lines (17) of which, a selectively vertically displaceable displacement-pump output function stored in the microprocessor controller (6) can be used for setting the proportional valve (7) via a microprocessor controller output line (18).
  • the proportional valve (7) is connected by setting lines (19) to the displacement pumps (2).
  • a solenoid valve (8) which, as a function of a signal of the microprocessor controller (6) on output lines (20), acts on the speed-of-rotation setting cylinder (14) on the diesel engine (1) via the lines (21).
  • the speed-of-rotation setting cylinder (14) is adjustable via a connection (22) as a function of deflection of the gas lever for the diesel engine (1).
  • a determinable magnitude deviation of an actual value can be pre-established.
  • FIGURE of the drawing shows a circuit digram of a control system of the hydraulic drive.
  • the present invention uses a known per se microprocessor controller 6.
  • the speed-of-rotation (rpm) of a diesel engine 1 of a construction machine for example is detected by means of a speed-of-rotation (rpm) generator 9 which is mechanically connected to the engine and fed to the microprocessor controller 6 as an input variable.
  • the temperature of the diesel engine 1, determined via a temperature sensor 10, is furthermore fed as an input variable to the microprocessor controller 6.
  • control lines 16 of pilot-control hand levers 12 of the construction machine are connected via change valves 13 to a pressure switch 11, the report of the position of the latter being fed as an input value to the microprocessor controller 6.
  • displacement pumps 2 mechanically driven by the engine via clutch 34 and gears are operated with a given pump output which corresponds to the engine speed of rotation.
  • the displacement pumps 2 are mechanically displaced as a result of the control oil pressure in the line 19 of an auxiliary control circuit.
  • Each pump has its own pump output curve of the quantity of oil produced (oil delivery output) vs. control oil pressure. This represents an inherent characteristic of the machine such as for example a construction machine.
  • the automatic control mechanism of the invention goes into action via the microprocessor controller 6 and, via line 18 and valve 7 or respectively line 19, sets back or reduces the hydraulic power given off by the displacement pumps 2.
  • This control process takes into account the particular event of overheating of the diesel engine 1.
  • the entry into normal operation of the displacement pumps 2 by the automatic system is referred to as a superposition function.
  • the arrows on the displacement pumps 2 express an angle of displacement with respect to the control hydraulic pressure of the valve 7 through the line 19.
  • the displacement pumps 2, which normally operate without displacement with full output, are set back by means of an auxiliary hydraulic control circuit 29.
  • a feedback line 28, indicated in dot-dash line, on the valve 7 provides a feed-back signal as to the oil pressure in the line 19 of the auxiliary control circuit 29 controlled via the valve 7 to the position of the valve 7. This provides a return message which stabilizes the position of the valve 7.
  • An auxiliary supply pump 4 coupled to be driven by the engine 1, feeds the hydraulic control circuit 29 for the setting of the load valves and auxiliary position transmitters.
  • the load control is then carried out by them separately with the delivered hydraulic output in lines 26 from output lines 2b from the displacement pumps 2.
  • the auxiliary supply pump 4 as can be noted from the drawing, inter alia, via the hand levers 12 or respectively the positions of their valves 12a, via the control lines 16, feeds a control block 27 of each load valve 12a.
  • the setting member for example a setting piston 24, is set there by the flow of control oil through the lines 16.
  • the setting piston 24 then, in its turn, by its position, releases to the load hydraulic circuit lines 26 the delivery oil from the output lines 2b of the displacement pumps 2 for respective work equipment, e.g. shovel 26a.
  • the lines 16 therefore go to respective control blocks 27 of each consumer load, for instance hydraulic cylinder 25 for the respective work equipment.
  • a memory of the microprocessor 6 there are programmed, pre-established as desired values for the operation of the displacement pumps 2, an output function of the displacement pumps as well as values to shift this output function vertically in accordance with the position of a selector switch 15 which thus changes the desired values within selectable regions.
  • the switch 15 in one position of the unnumbered contacts of the selector switch 15 can predetermine operation in the limit-output range as a desired value and in another position, via one connecting line 17, can shift the desired value to another, and particularly a lower, output range of the displacement pumps.
  • the selector switch 15 different output curves programmed in the memory are selected of delivery quantity of oil vs. control pressure of oil. For instance, in the illustrated position of the pointer of the selector switch 15, the highest obtainable value is established as the desired value for the microprocessor controller 6. In the next clockwise position, the connecting point of the line 17, a pump output characteristic curve is selected at half level, and in the third position, at one-quarter level as the desired value. Corresponding to the output of the microprocessor controller 6 thus produced, the proportional valve 7 is controlled via the microprocessor controller output line 18 and sets the displacement pumps 2 in the manner of the afore-mentioned superposition function.
  • the proportional valve 7 which is an electric solenoid valve controlled by the PID controller, also operates in the auxiliary control circuit 29 of the hydraulic circuit of the auxiliary supply pump 4. Depending on the extent of the opening of the valve 7 and via the line 19, the pump output of the displacement pumps 2 is varied.
  • the displacement of the displacement pumps 2 is effected by the control oil pressure in the line 19 against the pressure of a spring 2a on the displacement pumps 2. The higher the control pressure, the more the pump output of the displacement pumps 2 is displaced.
  • a solenoid valve 8 which is controlled by a signal from the microprocessor controller 6 in the line 20.
  • the solenoid valve 8 the hydraulic oil from the auxiliary supply pump 4 in the output line or circuit 29 acts on a speed-of-rotation (rpm) setting cylinder 14 on the diesel engine 1 via lines 21. This occurs in such a manner that the speed of rotation of the diesel engine 1 is brought back to the idling speed of rotation when the diesel engine 1 is subjected to a non-output loading for a selectably predeterminable time.
  • the hydraulic displacement pumps 2 are then operated with minimum delivery oil quantity.
  • the valves 12a of the hand-control levers 12 are known per se proportional valves. The more they are deflected by movement of the projecting levers, the greater is the hydraulic pressure fed to the control block 27 through the respective lines 16.
  • the valves 12a of the hand levers 12 feed the control block 27 of each consuming load in accordance with the deflection of the hand lever 12 via one or the other lines 16.
  • valves 12a are therefore arranged in pairs or two parts since upon flow, for instance, of a control hydraulic fluid in line 29 and operation of the hand-control levers 12, liquid flows over the right-hand one of the lines 16 to the setting member 23 and the oil displaced in the control block 27 from the setting member 23 on the opposite side flows back over the left-hand line 16 and the other valve 12a, in each case, into the oil sump 12b.
  • the hand levers 12 are moved by the operator of the construction machine.
  • the degree of their selection is converted, via the proportional valves 12a into setting commands for the connected consuming loads, for instance a hydraulic cylinder 25 for the shovel 26a or a hydraulic cylinder for the stick or boom of the excavator, etc.
  • the diesel engine 1 If no hydraulic output is required of the displacement pumps 2, i.e. no consuming load is connected to the hydraulic working circuit 26, then the diesel engine 1 operates approximately in the idling condition. In that case the solenoid valve 8 is in the position shown. From the auxiliary control hydraulic circuit 29 of the pump 4 which is driven by the engine 1, pressurized hydraulic oil flows via the solenoid valve 8 into the lower piston chamber 14b of the speed-of-rotation setting cylinder 14. Then the speed-of-rotation lever 33 (which may comprise the lever of a governor or be connected thereto) is located at the upper position shown, which represents its idling position for the engine 1. This speed-of-rotation lever 33 is located above the speed of rotation setting cylinder 14.
  • the speed-of-rotation lever 33 is set corresponding to the deflection position of a gas-pedal or gas-lever 32 for the diesel engine 1.
  • a mechanical connection is provided from the gas pedal or lever 32 out of the driver's cab of the construction machine to the speed-of-rotation lever 33 corresponding to connection train 22.
  • the speed of rotation connection train 22 can comprise a mechanical Bowden cable which extends from the gas lever 32 in the driver's cab of the construction machine to the lever 32 or to the piston 14a and is operated by the driver.
  • the speed-of-rotation connection lever 33 of the diesel engine 1 must be moved by means of the speed-of-rotation connection train 22 to a lower position.
  • the lever 33 is lowered downwardly via the speed-of-rotation connection train 22 by operation of the gas-lever 32 by the driver of the construction machine and effects a higher speed of rotation of the diesel engine 1.
  • the oil pressure of the control circuit 29 via the lines 21 as a function of the position of the solenoid valve 8.
  • the microprocessor controller 6 detects this via the open condition of switch 11 and a timer means (not shown) and sends a signal via the line 20, so as to shift the solenoid valve 8 back into the position shown in the drawing, and thus reduces the speed of rotation of the diesel engine 1.
  • a resetting of the solenoid valve 8 into the upper valve portion 8a line paths again takes place immediately.
  • a setting pump 3 is not included in the limit-load control. As indicated by the arrow shown at the pump 3 in the drawing, this displacement pump 3 is of course also controlled. Its control takes place, by means of a hand lever 30 via a Bowden cable 31 from the driver's cab.
  • the pump 3 feeds a separate consuming load, for instance a swing mechanism (turntable) 5 as diagrammatically indicated, with which, for instance, the turning movement of the construction machine, such as for instance an excavator, can be controlled with a special drive.
  • the microprocessor controller 6 receives measurements of the speed of rotation of the diesel engine 1 via the speed-of-rotation generator 9.
  • this speed of rotation which may be any desired speed of rotation and corresponds approximately to the idling speed of rotation of the diesel engine 1, is interpreted as the desired value by the microprocessor controller 6, since no action on the hydraulic circuit by pilot-control variables of the pilot control levers 12 is preset.
  • the controller 6 now interprets as an actual value the speed of rotation which is now measured by the rpm generator and carries out a comparison between the desired and actual values.
  • the desired value resulted from the measured value of the speed of rotation just before the closing of the pressure switch 11 and the engine characteristic diagram stored in the controller 6.
  • the microprocessor controller 6 detects this and then produces an electric PID signal which, via the microprocessor control output line 18 and the proportional valve 7, so effects a reduction in power of the displacement pumps 2 that the pump delivery flow in delivery lines 2b is reduced. This continues until no control deviation is present any longer which is detected by the controller 6 via the rpm generator 9. For carrying out the control of the displacement pumps 2, a deviation from the actual value corresponding to ordinary control process, is possible within given limits.
  • the diesel engine 1 is prevented from thermal overload in the manner that when a predetermined limit temperature set in the microprocessor controller 6 is detected by the temperature sensor 10, the displacement pumps 2 are reduced in their power consumption via and by a signal sent from the controller 6 to the proportional valve 7, until the temperature again drops below the limit temperature.
  • the microprocessor controller 6 sends, within the limit load control, a signal to the solenoid valve respectively the proportional valve 7 such that a larger auxiliary control hydraulic pressure resets the displacement pumps 2 via the line 19. In this way the diesel engine 1 is under less load driving the pumps 2 and the danger of overheating is reduced.
  • the microprocessor controller 6 determines that no hydraulic power is demanded via the pilot-control hand levers 12 then it sends to the solenoid valve 8 a signal which moves the solenoid valve 8 so that the control oil in line 29, via the speed of rotation setting cylinder 14 and lever 33, effects a reduction of the diesel engine rpm to idling. Furthermore, the microprocessor controller 6 sends a signal through line 18 which shifts the displacement pumps 2 to minimum delivery via the proportional valve 7.
  • not only the power engine 1 but also the entire hydraulic control system can be operated economically without being overheated, since the load applied to the engine is forced to decrease if overheated.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Component Parts Of Construction Machinery (AREA)
US07/035,546 1986-04-07 1987-04-07 Arrangement for operating a diesel hydraulic drive Expired - Lifetime US4763473A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3611553A DE3611553C1 (de) 1986-04-07 1986-04-07 Anordnung zum Betrieb eines dieselhydraulischen Antriebes
DE3611553 1986-04-07

Publications (1)

Publication Number Publication Date
US4763473A true US4763473A (en) 1988-08-16

Family

ID=6298083

Family Applications (1)

Application Number Title Priority Date Filing Date
US07/035,546 Expired - Lifetime US4763473A (en) 1986-04-07 1987-04-07 Arrangement for operating a diesel hydraulic drive

Country Status (7)

Country Link
US (1) US4763473A (fr)
JP (1) JPS62240439A (fr)
DE (1) DE3611553C1 (fr)
FR (1) FR2596807B1 (fr)
GB (1) GB2190217B (fr)
IT (1) IT1216798B (fr)
SE (1) SE462295B (fr)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5117632A (en) * 1989-04-10 1992-06-02 Linde Aktiengesellschaft Method of operating a drive unit
US5146746A (en) * 1989-11-20 1992-09-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Loading/unloading control apparatus for industrial vehicles
US5251440A (en) * 1990-11-13 1993-10-12 Samsung Heavy Industries Co., Ltd. Control apparatus and method for automatically controlling a hydraulic system for heavy construction equipment
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor
US5352095A (en) * 1992-06-10 1994-10-04 Shin Caterpillar Mitsubishi Ltd. Method for controlling hydraulic pump driven by engine
US5588474A (en) * 1995-06-07 1996-12-31 Vermeer Manufacturing Company Feed rate control system for stump cutters
WO1997047858A1 (fr) * 1996-06-10 1997-12-18 Tamrock Oy Procede et arrangement pour commander une unite de forage de roches entrainee par une source d'energie diesel-hydraulique
US5845689A (en) * 1995-06-07 1998-12-08 Vermeer Manufacturing Company Feed rate control system for stump cutters
US6014996A (en) * 1995-06-07 2000-01-18 Vermeer Manufacturing Company Control system for stump cutters
US6408876B1 (en) * 1998-12-01 2002-06-25 Hitachi Construction Machinery Co., Ltd. Control valve
US7490421B1 (en) 1999-08-21 2009-02-17 Herrn Georg Pletzer Method and construction machine for producing ground surfaces
US20090095527A1 (en) * 2007-10-16 2009-04-16 Lane Philip R Devices and Methods for Power Control in Horizontal Directional Drilling
US20100199656A1 (en) * 2005-05-18 2010-08-12 Ryota Ohashi Hydraulic Pump Unit
US20110056192A1 (en) * 2009-09-10 2011-03-10 Robert Weber Technique for controlling pumps in a hydraulic system
US20130174541A1 (en) * 2010-07-07 2013-07-11 Hinrich Meinheit Device and vehicle or production machine
US8606451B2 (en) 2010-10-06 2013-12-10 Caterpillar Global Mining Llc Energy system for heavy equipment
US8626403B2 (en) 2010-10-06 2014-01-07 Caterpillar Global Mining Llc Energy management and storage system
US8718845B2 (en) 2010-10-06 2014-05-06 Caterpillar Global Mining Llc Energy management system for heavy equipment
US9190852B2 (en) 2012-09-21 2015-11-17 Caterpillar Global Mining Llc Systems and methods for stabilizing power rate of change within generator based applications
US20160177886A1 (en) * 2014-12-22 2016-06-23 Mitsui Engineering & Shipbuilding Co., Ltd. Powering apparatus
JP2016133093A (ja) * 2015-01-21 2016-07-25 三菱重工業株式会社 液圧装置、内燃機関および船舶
EP2609288A4 (fr) * 2010-08-26 2018-01-17 Atlas Copco Rock Drills AB Procédé et système pour commander une source de puissance dans un appareil de forage de roche et appareil de forage de roche
US10066555B2 (en) 2015-03-30 2018-09-04 Caterpillar Forest Products Inc. Hydraulic system and method for controlling same
US20210388830A1 (en) * 2020-06-12 2021-12-16 Deere & Company Demand based hydraulic pump control system

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3611553C1 (de) * 1986-04-07 1987-07-23 Orenstein & Koppel Ag Anordnung zum Betrieb eines dieselhydraulischen Antriebes
DE3750677T2 (de) * 1986-08-15 1995-02-23 Komatsu Mfg Co Ltd Vorrichtung zur Steuerung einer hydraulischen Pumpe.
DE3911706C2 (de) * 1989-04-10 1999-09-30 Linde Ag Verfahren zum Betreiben einer Antriebseinheit
US5579931A (en) * 1989-10-10 1996-12-03 Manitowoc Engineering Company Liftcrane with synchronous rope operation
US5297019A (en) * 1989-10-10 1994-03-22 The Manitowoc Company, Inc. Control and hydraulic system for liftcrane
US5189605A (en) * 1989-10-10 1993-02-23 The Manitowoc Company, Inc. Control and hydraulic system for a liftcrane
US6758356B1 (en) 1989-10-10 2004-07-06 Manitowoc Crane Companies, Inc. Liftcrane with synchronous rope operation
JP2613131B2 (ja) * 1990-11-27 1997-05-21 株式会社小松製作所 油圧ポンプの出力制御装置
DE4309696C2 (de) * 1992-04-04 1995-01-05 Rexroth Mannesmann Gmbh Stellglied zur Steuerung der Drehzahl eines Brennkraftmotors
US5224836A (en) * 1992-05-12 1993-07-06 Ingersoll-Rand Company Control system for prime driver of compressor and method
DE19740346A1 (de) * 1997-09-13 1999-03-18 Claas Selbstfahr Erntemasch Selbstfahrende Arbeitsmaschine
DE102005017127B4 (de) 2005-04-14 2021-09-16 Linde Material Handling Gmbh Verbrennungsmotorisch betriebenes Flurförderzeug mit Überlastschutz
DE102006020441B4 (de) * 2006-05-03 2017-01-26 Bucyrus Hex Gmbh Verfahren zur Lastminderung eines oder mehrerer Motore in einem Groß-Hydraulikbagger

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4256439A (en) * 1978-11-20 1981-03-17 The Japan Steel Works Ltd. Power control system for multiple pumps
US4507057A (en) * 1980-01-07 1985-03-26 Kabushiki Kaisha Komatsu Seisakusho Control system for hydraulic pumps of a civil machine
US4596517A (en) * 1985-01-29 1986-06-24 Poclain Pressurized fluid supply circuit comprising a variable displacement pump
US4600364A (en) * 1983-06-20 1986-07-15 Kabushiki Kaisha Komatsu Seisakusho Fluid operated pump displacement control system

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4017216A (en) * 1976-03-15 1977-04-12 Caterpillar Tractor Co. Variable underspeed system linkage
US4606313A (en) * 1980-10-09 1986-08-19 Hitachi Construction Machinery Co., Ltd. Method of and system for controlling hydraulic power system
DE3560243D1 (en) * 1984-03-30 1987-07-16 Komatsu Mfg Co Ltd Method and system for controlling an engine
DE3611553C1 (de) * 1986-04-07 1987-07-23 Orenstein & Koppel Ag Anordnung zum Betrieb eines dieselhydraulischen Antriebes

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4256439A (en) * 1978-11-20 1981-03-17 The Japan Steel Works Ltd. Power control system for multiple pumps
US4507057A (en) * 1980-01-07 1985-03-26 Kabushiki Kaisha Komatsu Seisakusho Control system for hydraulic pumps of a civil machine
US4600364A (en) * 1983-06-20 1986-07-15 Kabushiki Kaisha Komatsu Seisakusho Fluid operated pump displacement control system
US4596517A (en) * 1985-01-29 1986-06-24 Poclain Pressurized fluid supply circuit comprising a variable displacement pump

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Hydraulics", Hitachi Co. publication, Jan. 5, 1987.
Hydraulics , Hitachi Co. publication, Jan. 5, 1987. *

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5117632A (en) * 1989-04-10 1992-06-02 Linde Aktiengesellschaft Method of operating a drive unit
US5146746A (en) * 1989-11-20 1992-09-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Loading/unloading control apparatus for industrial vehicles
US5251440A (en) * 1990-11-13 1993-10-12 Samsung Heavy Industries Co., Ltd. Control apparatus and method for automatically controlling a hydraulic system for heavy construction equipment
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor
US5352095A (en) * 1992-06-10 1994-10-04 Shin Caterpillar Mitsubishi Ltd. Method for controlling hydraulic pump driven by engine
US6014996A (en) * 1995-06-07 2000-01-18 Vermeer Manufacturing Company Control system for stump cutters
US5845689A (en) * 1995-06-07 1998-12-08 Vermeer Manufacturing Company Feed rate control system for stump cutters
US5588474A (en) * 1995-06-07 1996-12-31 Vermeer Manufacturing Company Feed rate control system for stump cutters
WO1997047858A1 (fr) * 1996-06-10 1997-12-18 Tamrock Oy Procede et arrangement pour commander une unite de forage de roches entrainee par une source d'energie diesel-hydraulique
US6408876B1 (en) * 1998-12-01 2002-06-25 Hitachi Construction Machinery Co., Ltd. Control valve
US7490421B1 (en) 1999-08-21 2009-02-17 Herrn Georg Pletzer Method and construction machine for producing ground surfaces
US20100199656A1 (en) * 2005-05-18 2010-08-12 Ryota Ohashi Hydraulic Pump Unit
US20090095527A1 (en) * 2007-10-16 2009-04-16 Lane Philip R Devices and Methods for Power Control in Horizontal Directional Drilling
WO2009052304A1 (fr) * 2007-10-16 2009-04-23 Vermeer Manufacturing Company Dispositifs et procédés pour commande de puissance dans le forage directionnel horizontal
US7954558B2 (en) 2007-10-16 2011-06-07 Vermeer Manufacturing Company Devices and methods for power control in horizontal directional drilling
US20110056192A1 (en) * 2009-09-10 2011-03-10 Robert Weber Technique for controlling pumps in a hydraulic system
US20130174541A1 (en) * 2010-07-07 2013-07-11 Hinrich Meinheit Device and vehicle or production machine
US9212601B2 (en) * 2010-07-07 2015-12-15 Robert Bosch Gmbh Device and vehicle or production machine
EP2609288A4 (fr) * 2010-08-26 2018-01-17 Atlas Copco Rock Drills AB Procédé et système pour commander une source de puissance dans un appareil de forage de roche et appareil de forage de roche
US8626403B2 (en) 2010-10-06 2014-01-07 Caterpillar Global Mining Llc Energy management and storage system
US8718845B2 (en) 2010-10-06 2014-05-06 Caterpillar Global Mining Llc Energy management system for heavy equipment
US9120387B2 (en) 2010-10-06 2015-09-01 Caterpillar Global Mining Llc Energy management system for heavy equipment
US8606451B2 (en) 2010-10-06 2013-12-10 Caterpillar Global Mining Llc Energy system for heavy equipment
US9190852B2 (en) 2012-09-21 2015-11-17 Caterpillar Global Mining Llc Systems and methods for stabilizing power rate of change within generator based applications
US20160177886A1 (en) * 2014-12-22 2016-06-23 Mitsui Engineering & Shipbuilding Co., Ltd. Powering apparatus
US9874180B2 (en) * 2014-12-22 2018-01-23 Mitsui Engineering & Shipbuilding Co., Ltd. Powering apparatus
WO2016117156A1 (fr) * 2015-01-21 2016-07-28 三菱重工業株式会社 Dispositif hydraulique, moteur à combustion interne et navire
CN107208624A (zh) * 2015-01-21 2017-09-26 三菱重工业株式会社 液压装置、内燃机以及船舶
JP2016133093A (ja) * 2015-01-21 2016-07-25 三菱重工業株式会社 液圧装置、内燃機関および船舶
CN107208624B (zh) * 2015-01-21 2019-01-08 三菱重工业株式会社 液压装置、内燃机以及船舶
US10066555B2 (en) 2015-03-30 2018-09-04 Caterpillar Forest Products Inc. Hydraulic system and method for controlling same
US20180347480A1 (en) * 2015-03-30 2018-12-06 Caterpillar Forest Products Inc. Hydraulic system and method for controlling same
US10837375B2 (en) * 2015-03-30 2020-11-17 Caterpillar Forest Products Inc. Hydraulic system and method for controlling same
US20210388830A1 (en) * 2020-06-12 2021-12-16 Deere & Company Demand based hydraulic pump control system

Also Published As

Publication number Publication date
JPS62240439A (ja) 1987-10-21
GB2190217B (en) 1989-12-06
DE3611553C1 (de) 1987-07-23
GB8707965D0 (en) 1987-05-07
FR2596807B1 (fr) 1990-07-13
SE462295B (sv) 1990-05-28
SE8605265L (sv) 1987-10-08
GB2190217A (en) 1987-11-11
FR2596807A1 (fr) 1987-10-09
IT1216798B (it) 1990-03-14
SE8605265D0 (sv) 1986-12-09
IT8747717A0 (it) 1987-03-12

Similar Documents

Publication Publication Date Title
US4763473A (en) Arrangement for operating a diesel hydraulic drive
US5285642A (en) Load sensing control system for hydraulic machine
US5155996A (en) Hydraulic drive system for construction machine
EP0062072B1 (fr) Procede de commande d'un systeme hydraulique
CN101568692B (zh) 液压工程机械的泵扭矩控制装置
EP0765970B1 (fr) Dispositif de commande hydraulique pour engin de chantier
US4967557A (en) Control system for load-sensing hydraulic drive circuit
US4884402A (en) Control and regulating device for a hydrostatic drive assembly and method of operating same
KR100527824B1 (ko) 휠식 유압 주행 차량의 속도 제어 장치
EP0287670B1 (fr) Dispositif de commande d'entrainement pour machines de construction hydrauliques
US5535587A (en) Hydraulic drive system
KR100760129B1 (ko) 작업 차량의 제어 장치
CA2251107C (fr) Procede et dispositif de commande d'un ascenseur hydraulique
US6305419B1 (en) Variable pilot pressure control for pilot valves
US5295353A (en) Controlling arrangement for travelling work vehicle
US7894963B2 (en) System and method for controlling a machine
CN101932814A (zh) 发动机的控制装置及其控制方法
US5101629A (en) Hydraulic circuit system for working machine
US4464898A (en) Hydraulic power system
US4884475A (en) Automotive drive system for machines and vehicles
JP2651079B2 (ja) 油圧建設機械
US5117632A (en) Method of operating a drive unit
EP0491944B1 (fr) Unite de commande de changement de vitesse d'un moteur hydraulique en marche
CA1221152A (fr) Systeme hydraulique de commande a compensateur
JP2001295682A (ja) 油圧走行車両

Legal Events

Date Code Title Description
AS Assignment

Owner name: O&K ORENSTEIN & KOPPEL AKTIENGESELLSCHAFT, KARL FU

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:ZIPLIES, HERBERT;LACKENBERG, HEINRICH;REEL/FRAME:004726/0027

Effective date: 19870605

STCF Information on status: patent grant

Free format text: PATENTED CASE

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

FPAY Fee payment

Year of fee payment: 12

REMI Maintenance fee reminder mailed
AS Assignment

Owner name: CNH BAUMASCHINEN GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:O&K ORENSTEIN & KOPPEL;REEL/FRAME:017776/0281

Effective date: 20060614